EP0780596A2 - Transmisson de changement de vitesse sous charge avec arbre intermédiaire - Google Patents

Transmisson de changement de vitesse sous charge avec arbre intermédiaire Download PDF

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Publication number
EP0780596A2
EP0780596A2 EP96118876A EP96118876A EP0780596A2 EP 0780596 A2 EP0780596 A2 EP 0780596A2 EP 96118876 A EP96118876 A EP 96118876A EP 96118876 A EP96118876 A EP 96118876A EP 0780596 A2 EP0780596 A2 EP 0780596A2
Authority
EP
European Patent Office
Prior art keywords
gear
clutch
friction clutch
transmission
input shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP96118876A
Other languages
German (de)
English (en)
Other versions
EP0780596A3 (fr
EP0780596B1 (fr
Inventor
Christian Krauss
Thomas Wollny
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ford Global Technologies LLC
Original Assignee
Ford Werke GmbH
Ford France SA
Ford Motor Co Ltd
Ford Motor Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ford Werke GmbH, Ford France SA, Ford Motor Co Ltd, Ford Motor Co filed Critical Ford Werke GmbH
Publication of EP0780596A2 publication Critical patent/EP0780596A2/fr
Publication of EP0780596A3 publication Critical patent/EP0780596A3/fr
Application granted granted Critical
Publication of EP0780596B1 publication Critical patent/EP0780596B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/02—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of clutch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • F16H2003/007—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths with two flow paths, one being directly connected to the input, the other being connected to the input though a clutch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H2003/0818—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts comprising means for power-shifting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/04—Smoothing ratio shift
    • F16H61/0403—Synchronisation before shifting
    • F16H2061/0407—Synchronisation before shifting by control of clutch in parallel torque path
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0047—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising five forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/12—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with means for synchronisation not incorporated in the clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/04—Smoothing ratio shift
    • F16H61/0437—Smoothing ratio shift by using electrical signals
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19023—Plural power paths to and/or from gearing
    • Y10T74/19037—One path includes fluid drive
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y10T74/19233—Plurality of counter shafts
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y10T74/19242—Combined gear and clutch

Definitions

  • the invention relates to a countershaft transmission for motor vehicles that can be switched without interruption in tractive power, of the type explained in the preamble of patent claim 1.
  • DE-OS 40 31 851 discloses a countershaft transmission for motor vehicles which can be switched without interruption in tractive power and which is known in the preamble of claim 1.
  • a direct, driving connection to a first transmission input shaft is provided between a flywheel, which forms the input part of a friction clutch, and the output part of the friction clutch is connected to a second gear input shaft comprising the first transmission input shaft in the form of a hollow shaft.
  • the fixed gear wheels of the gear stages are essentially on the first transmission input shaft and the idler gears of the gear stages are arranged on a countershaft arranged parallel to the two transmission input shafts, claw or synchronous clutches being arranged between paired idler wheels on the countershaft in order to separate the individual gear stages switch.
  • the fixed gears of the lowest and the highest gear stage are arranged on the second transmission input shaft and, in contrast to the other gear stages, the fixed gear is arranged on the countershaft and the idler gear on the first transmission input shaft at the second highest gear stage.
  • the known countershaft transmission has the disadvantage that the disengagement of the friction clutch required at the beginning of the shift from 1st gear to 2nd gear causes a brief interruption in the tractive force, which can lead to an undesired revving of the internal combustion engine.
  • EP-PS 0 173 117 discloses a countershaft transmission for motor vehicles which can be switched without interruption in tractive power, in which a drive motor drives a first transmission input shaft via a direct connection, on which a plurality of fixed gears of gear stages are arranged and in parallel with which a countershaft is arranged , on which a plurality of idler gears for the different gear stages are arranged, a claw or synchronous clutch being arranged between paired idler gears.
  • the transmission input shaft which is connected directly to the drive motor, the input part of a friction clutch is rotatably connected, the output part of which is connected to a second transmission input shaft in the form of a hollow shaft on which the fixed gears of the 5th gear and reverse gear are arranged.
  • a starting process of the motor vehicle is started by inserting the sliding sleeve into 5th gear, the friction clutch being disengaged first. Subsequently, the friction clutch is now controlled, i.e. engaged by sliding, in such a way that as soon as the engagement speed for 1st gear is reached, the sliding sleeve can be inserted smoothly into 1st gear and the friction clutch is then disengaged, since the torque is transmitted via the gear set of the 1st gear. To engage the 2nd gear, the friction clutch is engaged again in a controlled manner, so that the engagement speed of the 2nd gear can be adjusted, whereupon when this speed is reached, the sliding sleeve for the 2nd gear is moved to the gear set for the 2nd Bring gear into torque transmission. The friction clutch is then disengaged again.
  • the known countershaft transmission has the disadvantage that, since the starting process via the gear stage of the highest gear, e.g. 5th gear is carried out, the friction clutch must have a considerable friction or slippage, which usually no longer the simple single-disc friction clutch usual in force products can be used, but a wet multi-disc friction clutch running in lubricating oil must be used.
  • the object of the invention is to improve a countershaft transmission of the type explained in the preamble of claim 1 in such a way that using the simpler Single-disc friction clutch enables gear shift-free shifting of all gear stages without torque interruption in the critical starting area when changing gear between 1st and 2nd gear.
  • the starting process can be carried out via the controlled friction clutch and the translation of the 1st Ganges take place, whereupon only the direct connection between the input part of the friction clutch and the first transmission input shaft is established by the switchable claw clutch.
  • FIG. 1 The construction of the countershaft transmission according to the invention is explained in connection with FIG. 1, in which the individual transmission elements are provided with corresponding reference numerals, which are repeated in the further FIGS. 2 to 8 only with the difference that the transmission parts engaged in the torque path in their switched positions are drawn and the flow of force is indicated by reinforced lines.
  • a drive motor 1 preferably an internal combustion engine with a crankshaft 2 drives a flywheel 3, which is connected in a conventional manner to a friction disk clutch 4, which essentially consists of an input element 5 and an output element 6.
  • the countershaft change transmission consists of a first transmission input shaft 7 and a second transmission input shaft 8, the second transmission input shaft being designed as a hollow shaft 8 comprising the first input shaft 7.
  • Gear sets for the gears 1 to 5 are arranged in the countershaft transmission, preferably the fixed gears 9, 11, 13 and 15 are arranged on the first transmission input shaft 7 and their counter gears or idler gears 10, 12, 14 and 16 on one parallel to the transmission input shafts 7 and 8 arranged countershaft 17 are arranged.
  • the countershaft 17 is connected to a final drive 18.
  • the fixed gear 19 is fixed on the countershaft 17 and the idler gear 20 is arranged on the second transmission input shaft 8.
  • Synchronizer clutches with corresponding sliding sleeves 21 and 22 are arranged between two adjacent idler gears 10 and 12 or 14 and 16 in a manner known per se.
  • the direct connection between the flywheel 3 and the first transmission input shaft 7 is designed as a switchable claw clutch 23 and the output element 6 of the friction clutch 4 is not in direct driving connection with the first transmission input shaft 7, but is above it a switchable synchronous clutch 24 or connectable to the idler gear 20 arranged on the hollow shaft 8 of the 5th gear.
  • the friction clutch 4 is disengaged and in its place the dog clutch 23 is engaged, which is a direct one driving connection between the flywheel 3 and the first transmission input shaft 7.
  • the further torque flow remains above the gear set of the 1st gear and its synchronous clutch on the countershaft and the final drive.
  • the synchronizing clutch 24 is first brought into engagement with the idler gear 20 of the 5th gear and then the friction clutch 4 is engaged in a controlled manner, until the torque flow running through the gear set of the 5th gear relieves the load on the gear set of the 1st gear, as a result of which, as can be seen from FIG. 5, it switches into the neutral position and then into the position for the 2nd gear shown in FIG. 6 can be. Following this circuit, the friction clutch 4 is disengaged again and the torque transmission flow runs through the dog clutch 23 and the gear set of the 2nd gear.
  • the friction clutch 4 is again engaged in a controlled manner, whereby it transmits torque via the still engaged synchronizing clutch 24 to the idler gear 20 of the 5th gear and until the gear set again of the 2nd gear becomes torque-free because the 5th gear engaged with the sliding clutch takes over the torque transmission. Therefore, the synchromesh clutch can again be shifted from the position of the 2nd gear into the neutral position and then into the position for the 1st gear without any problems, and by disengaging the friction clutch 4, a torque flow is subsequently produced again via the dog clutch 23 and the gear set of the 1st Ganges provided.
  • the inventive design of the countershaft gearbox has the advantage that the starting process is over the gear set of the 1st gear can take place and at the same time the additional clutches 23 and 24 ensure that when the gear is changed from 1st gear to 2nd gear and the necessary disengagement of the friction clutch 4, the drive motor cannot run away.
  • the output element of the friction clutch can be connected via further clutches either to the idler gear of the highest gear, to the first transmission input shaft or to any other idler gear of a gear.
  • the output element of the friction clutch can also be connected to any idler gears or to the first transmission input shaft via further clutches.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Structure Of Transmissions (AREA)
EP96118876A 1995-12-23 1996-11-26 Transmisson de changement de vitesse sous charge avec arbre intermédiaire Expired - Lifetime EP0780596B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19548622A DE19548622C1 (de) 1995-12-23 1995-12-23 Zugkraftunterbrechungsfrei schaltbares Vorgelege-Wechselgetriebe für Kraftfahrzeuge
DE19548622 1995-12-23

Publications (3)

Publication Number Publication Date
EP0780596A2 true EP0780596A2 (fr) 1997-06-25
EP0780596A3 EP0780596A3 (fr) 1998-12-16
EP0780596B1 EP0780596B1 (fr) 2001-08-01

Family

ID=7781336

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96118876A Expired - Lifetime EP0780596B1 (fr) 1995-12-23 1996-11-26 Transmisson de changement de vitesse sous charge avec arbre intermédiaire

Country Status (3)

Country Link
US (1) US5761961A (fr)
EP (1) EP0780596B1 (fr)
DE (2) DE19548622C1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19924501A1 (de) * 1999-05-28 2000-12-28 Daimler Chrysler Ag Lastschaltbares Stufenwechselgetriebe
EP1260738A1 (fr) * 2001-05-23 2002-11-27 Fuji Jukogyo Kabushiki Kaisha Boite robotisée avec un embrayage de passage à friction
EP2404079A1 (fr) * 2009-03-06 2012-01-11 DTI Group B.V. Transmission pour un entraînement électrique ou hybride
FR2965030A1 (fr) * 2010-09-20 2012-03-23 Renault Sas Transmission automatique a double embrayage a rapport unique sur l'arbre creux

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DE19802819C2 (de) * 1998-01-26 2003-01-23 Getrag Getriebe Zahnrad Kraftfahrzeug-Antriebsstrang
DE19802820C1 (de) * 1998-01-26 1999-12-16 Getrag Getriebe Zahnrad Kraftfahrzeug-Stufengetriebe
DE19837776A1 (de) * 1998-08-20 2000-02-24 Zahnradfabrik Friedrichshafen Getriebe mit nicht-koaxialem Abtrieb
EP0984202B1 (fr) * 1998-08-25 2002-07-31 Ford Global Technologies, Inc., A subsidiary of Ford Motor Company Boíte de vitesses du type à trois arbres pour véhicules automobiles
DE19853824A1 (de) * 1998-11-21 2000-05-31 Getrag Getriebe Zahnrad Automatisierbarer Kraftfahrzeug-Antriebsstrang sowie Verfahren zum Steuern eines solchen Antriebsstranges
DE19853825C1 (de) 1998-11-21 2000-01-27 Getrag Getriebe Zahnrad Kraftfahrzeug-Antriebsstrang und Verfahren zum Steuern eines Schaltvorganges eines Kraftfahrzeug-Antriebsstranges
DE19905273A1 (de) * 1999-02-09 2000-08-24 Getrag Getriebe Zahnrad Automatisierbarer Antriebsstrang für ein Kraftfahrzeug
JP2001213201A (ja) * 1999-12-17 2001-08-07 Getrag Getriebe & Zahnradfab Hermann Hagenmeyer Gmbh & Co 自動車のための自動的な駆動機構列並びに駆動機構列を制御する方法
WO2001088409A2 (fr) * 2000-05-17 2001-11-22 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Transmission comprenant un embrayage et procede pour actionner un embrayage
JP4669172B2 (ja) * 2001-09-05 2011-04-13 株式会社ワイ．ジー．ケー 可変質量フライホイール
JP3712660B2 (ja) * 2001-11-15 2005-11-02 本田技研工業株式会社 動力伝達装置
DE10203514A1 (de) 2002-01-30 2003-08-07 Bosch Gmbh Robert Vorlege-Wechselgetriebe für Kraftfahrzeuge
AU2003223881A1 (en) * 2002-04-05 2003-10-20 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Power shift transmission and method for controlling a twin clutch transmission
JP4260522B2 (ja) * 2002-04-24 2009-04-30 本田技研工業株式会社 動力伝達装置
DE10361333A1 (de) * 2003-12-18 2005-07-14 Getrag Innovations Gmbh Automatisches Wechselgetriebe
DE102004041525B4 (de) * 2004-08-27 2012-01-26 Gm Global Technology Operations Llc (N.D.Ges.D. Staates Delaware) Lastschaltgetriebe und Schaltverfahren dafür
US7246536B2 (en) * 2005-03-17 2007-07-24 Ford Global Technologies, Llc Dual clutch kinematic arrangements with wide span
DE102008002295A1 (de) 2008-06-09 2009-12-10 Zf Friedrichshafen Ag Mehrgruppengetriebe eines Kraftfahrzeuges
DE102009003108B4 (de) * 2009-05-14 2017-08-10 Zf Friedrichshafen Ag Antriebsanordnung mit zwei eingangsseitigen Kupplungen
GB2479769A (en) * 2010-04-21 2011-10-26 Gm Global Tech Operations Inc Automatic transmission having three clutches
US8960032B2 (en) 2010-06-02 2015-02-24 Volvo Lastvagnar Ab Multi-clutch transmission for a motor vehicle
DE102011011171A1 (de) * 2011-02-14 2012-08-16 Audi Ag Antriebsanordnung für ein Kraftfahrzeug
FR2973091A1 (fr) * 2011-03-23 2012-09-28 Peugeot Citroen Automobiles Sa Boite de vitesses pilotee pour vehicule a moteur
DE102012001948A1 (de) * 2012-02-02 2013-08-08 Daimler Ag Doppelkupplungsgetriebe
CN102748465A (zh) * 2012-07-18 2012-10-24 鲁伟 一种带有换挡辅助轴的变速箱和其换挡方法
JP5545778B2 (ja) * 2012-08-08 2014-07-09 富士重工業株式会社 変速機
US20150158382A1 (en) 2013-12-05 2015-06-11 Avl Powertrain Engineering, Inc. Two-speed transmission for electric vehicle
US9740240B1 (en) 2016-03-21 2017-08-22 Google Inc. Base with rotating mount that increases friction of rotation when portable computing device is placed onto mount

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DE4017961A1 (de) * 1989-06-10 1990-12-13 Zahnradfabrik Friedrichshafen Steuersystem fuer ein lastschaltbares doppel-kupplungsgetriebe
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Publication number Priority date Publication date Assignee Title
DE3715880A1 (de) * 1987-05-13 1988-05-19 Bayerische Motoren Werke Ag Stirnraederwechselgetriebe fuer kraftfahrzeuge, insbesondere personenkraftwagen
DE4017961A1 (de) * 1989-06-10 1990-12-13 Zahnradfabrik Friedrichshafen Steuersystem fuer ein lastschaltbares doppel-kupplungsgetriebe
DE4031851A1 (de) * 1990-10-08 1992-04-09 Volkswagen Ag Stufenwechselgetriebe
DE4401812A1 (de) * 1993-02-03 1994-08-04 Volkswagen Ag Stufenwechselgetriebe

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19924501A1 (de) * 1999-05-28 2000-12-28 Daimler Chrysler Ag Lastschaltbares Stufenwechselgetriebe
EP1260738A1 (fr) * 2001-05-23 2002-11-27 Fuji Jukogyo Kabushiki Kaisha Boite robotisée avec un embrayage de passage à friction
US6793604B2 (en) 2001-05-23 2004-09-21 Fuji Jukogyo Kabushiki Kaisha Automatic transmission
EP2404079A1 (fr) * 2009-03-06 2012-01-11 DTI Group B.V. Transmission pour un entraînement électrique ou hybride
EP2404079B1 (fr) * 2009-03-06 2014-12-03 DTI Group B.V. Transmission pour un entraînement électrique ou hybride
FR2965030A1 (fr) * 2010-09-20 2012-03-23 Renault Sas Transmission automatique a double embrayage a rapport unique sur l'arbre creux

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EP0780596A3 (fr) 1998-12-16
US5761961A (en) 1998-06-09
DE59607410D1 (de) 2001-09-06
DE19548622C1 (de) 1997-05-07
EP0780596B1 (fr) 2001-08-01

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